US20100288953A1 - Pressure Balance Of Automotive Air Bypass Valve - Google Patents
Pressure Balance Of Automotive Air Bypass Valve Download PDFInfo
- Publication number
- US20100288953A1 US20100288953A1 US12/812,603 US81260309A US2010288953A1 US 20100288953 A1 US20100288953 A1 US 20100288953A1 US 81260309 A US81260309 A US 81260309A US 2010288953 A1 US2010288953 A1 US 2010288953A1
- Authority
- US
- United States
- Prior art keywords
- armature
- seal
- port
- coil
- constructed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M23/00—Apparatus for adding secondary air to fuel-air mixture
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0686—Braking, pressure equilibration, shock absorbing
- F16K31/0693—Pressure equilibration of the armature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/16—Control of the pumps by bypassing charging air
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
- H01F7/00—Magnets
- H01F7/06—Electromagnets; Actuators including electromagnets
- H01F7/08—Electromagnets; Actuators including electromagnets with armatures
- H01F7/16—Rectilinearly-movable armatures
- H01F7/1607—Armatures entering the winding
- H01F7/1623—Armatures having T-form
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the embodiment relates to a solenoid device for the bypass of intake air in an automotive application and, more particularly, to an air bypass valve that has passive internal pressure balancing.
- Automotive applications typically using an air pump, specifically a turbine, supercharger, or exhaust driven turbocharger include gasoline, natural gas or diesel internal combustion engines. Other automotive applications also include fuel cells and fuel reformers, both requiring large volumes of air and often supplied by a turbine pump. While a bypass valve may be utilized for any pump configuration, the exhaust driven turbocharger is the typical application.
- the exhaust driven turbocharger is a free-spinning turbine with a shaft-separated split impeller, one end receiving force and a rotational moment from the exiting exhaust gases, the other end applying a pumping effect.
- bypass valve For the purpose of reducing the load on the turbocharger during sudden decreases of downstream flow, a bypass valve is typically applied to allow the impeller to continue moving air from the low pressure side to the high pressure side at a rate now set by the impeller speed. It is desirable to have a valve which can respond quickly when deceleration, load change or load shift point occurs, and recover quickly as when acceleration or higher load is suddenly required. When not energized, it is desirable to minimize bypass leak and corresponding decrease in pump efficiency when full throughput is required from pump. This must be satisfied with robustness as well as cost efficiency, while at the same time not introducing undesirable noise, vibration and harshness, or noise, vibration, harshness (NVH).
- bypass valves are comparatively large, heavy electromagnets with machined parts and multiple elastomeric diaphragms, bumpers and seals.
- An object of the present invention is to fulfill the need referred to above.
- this objective is obtained by providing a pressure-balanced solenoid device including a solenoid assembly having a stator and a coil constructed and arranged to be energized to generate a magnetic field.
- An armature and seal assembly includes an armature structure constructed and arranged to move with respect to the solenoid assembly from a closed position, defining a working gap area between the coil and a portion of the armature structure, to an open position in response to the magnetic field generated by the coil.
- the armature structure includes a proximal end and a distal end.
- the armature and seal structure also includes a seal structure coupled with proximal end of the armature structure.
- the seal structure has a sealing edge constructed and arranged to seal with a component when the armature structure is in the closed position thereof.
- a spring biases the armature structure to the closed position.
- the armature and seal assembly includes pressure balancing structure constructed and arranged to provide a pressure balance between the working gap area and an area defined adjacent to 1) the sealing edge, and 2) the distal end of the armature structure.
- the solenoid device may be an air bypass valve for an automobile.
- a method of balancing pressure in a solenoid device provides a solenoid assembly including a stator and a coil constructed and arranged to be energized to generate a magnetic field.
- An armature structure is provided and is constructed and arranged to move with respect to the solenoid assembly from a closed position, defining a working gap area between the coil and a portion of the armature structure, to an open position in response to the magnetic field generated by the coil.
- the armature structure includes a proximal end and a distal end.
- a seal structure is coupled with proximal end of the armature structure.
- the seal structure has a sealing edge constructed and arranged to seal with a component when the armature structure is in the closed position thereof.
- the armature structure is biased to the closed position.
- FIG. 1 is a view of a solenoid device in the form of an automotive air bypass valve in accordance with an embodiment of the present invention.
- FIG. 2 is an exploded view of an armature and seal assembly of the air bypass valve of FIG. 1 .
- FIG. 3 is an assembled view of the armature and seal assembly of FIG. 2 .
- FIG. 4 is an exploded view of a solenoid assembly of the air bypass valve of FIG. 1 .
- FIG. 5 is an assembled view of the solenoid assembly of FIG. 4 .
- FIG. 6 is an exploded view of the armature assembly being inserted into the overmolded solenoid assembly of the air bypass valve of FIG. 1 .
- FIG. 7 is a sectional view of a solenoid device of FIG. 1 shown with an armature in a closed position.
- FIG. 8 is a view of the solenoid device of FIG. 7 , with the armature shown in an open position.
- a solenoid device in the form of an air bypass valve for a vehicle is shown, generally indicated at 10 , in accordance with an embodiment of the invention.
- the air bypass valve detailed herein comprises about fourteen basic parts, potentially none of which are machined, but all of which are preferably injection molded, stamped, or drawn from sheet stock. Such a configuration provides a realized savings in used material volume and type, along with the corresponding environmental and economic benefits.
- the armature and seal assembly 12 is the moving component of the valve 10 and includes an armature structure having an armature 14 and a composite, resin or polymer molded pivot gland structure 16 either molded onto a proximal end 15 of the armature 14 or assembled thereto with a mechanical retainer (not shown).
- the gland structure 16 can be considered to be part of the armature 14 and includes a gland member 18 , the function of which will be explained below.
- a dynamic seal 20 of an appropriate material is either incorporated as part of the gland structure 16 , co-injection molded therewith, or coupled thereto as a separate component.
- a hard seal structure 22 preferably made of similar materials as the gland structure 16 , has a pivot member 23 that is preferably snapped together with the gland member 18 .
- the mating co-centric spherical surfaces (external surface 24 of gland member 18 and internal surface 26 of the pivot member 23 ) form a pivot function such that the seal structure 22 can pivot with respect to the gland structure 16 and thus the armature 14 .
- the 360° pivot function is accommodates any dimensional variance from ideal between the axis of the solenoid assembly 30 , mounting face of the complete assembly and the sealing surface and mounting surfaces of the respective air manifold or component to which the valve assembly 10 is attached. By accommodating these variances, bypass leak is minimized and durable function of the solenoid maximized in allowing the hard sealing edge 28 of the hard seal structure 22 to mate with the opposite mounting sealing surface as parallel as possible. It is noted that the inner spherical surface can be part of the gland member with the outer spherical surface being part of the pivot member 23 .
- solenoid assembly generally indicated at 30 .
- the solenoid assembly 30 includes the stationary magnetic components of the valve 10 and includes a magnetic (e.g., ferrous) housing 32 that provides a flux return path and a datum enclosure for other parts of the valve 10 .
- a coil bobbin 34 is wound with an electromagnet coil 36 of a suitable wire material of an appropriate number of turns to provide the resistance and ampere-turns necessary for proper function with the available control electronics.
- the coil 36 is not shown in FIG. 4 .
- the coil bobbin 34 with coil 36 is inserted into the housing 32 , and a magnetic (e.g., ferrous) flux ring 38 is pressed into the housing 32 , retaining the coil bobbin 34 and providing a specific working magnetic pole-type to the armature 14 .
- a spring pin 40 is provided in the housing 32 and a magnetic (e.g., ferrous) end cap 42 is pressed onto the housing 32 , thereby retaining the spring pin 40 .
- the spring pin 40 is received in a bore 41 in a stem portion 55 of the armature 14 so that a first end 43 of the spring pin 40 engages the spring 44 and a second end 45 of the spring pin 40 is adjacent to the end cap 42 .
- the spring pin 40 provides an axial flux path into the armature 14 as well as guides a closing return spring 44 , also in bore 41 , in the final assembly.
- the stator of the solenoid assembly 30 comprises the lump magnetic circuit formed by the magnetic flux ring 38 , the magnetic housing 32 , the magnetic end cap 42 and, if desired, the spring pin 40 .
- the solenoid assembly 30 is over-molded with an appropriate polymer or resin to provide the final encapsulation and retention main housing 46 of all stationary parts for the air bypass valve 10 .
- FIG. 6 shows the final assembly of the valve 10 and also shows how the encapsulation provides a customer specified flange 48 for mounting by the end user.
- the flange 48 includes mounting holes 50 that receive, preferably in an encapsulated manner, a support boss 52 therein.
- the main housing 46 includes impact protection structure that protect the armature and seal assembly 12 from drops and handling, as well as any manifold sealing O-rings.
- the impact protection structure includes a plurality of tabs 54 extending in an annular manner from a bottom surface 56 of the housing 46 so as to generally surround the seal structure 22 of the armature and seal assembly 12 .
- the closing return spring 44 is inserted into the armature 14 , and the armature and seal assembly 12 is the inserted into the solenoid assembly 30 . More particularly, a stem portion 55 of the armature 14 is received in a bore 57 in the coil bobbin 34 .
- An O-ring 58 provides a seal with respect to an air manifold (not shown) to which the valve 10 is attached.
- FIG. 7 shows the closed position the valve 10 and armature 14 (biased by spring 44 ) when the electromagnetic coil 36 is not energized via leads 60 .
- the magnetic gap working volume area 62 is clearly shown between the coil 36 and a generally cylindrical base 63 of the armature 14 .
- the sealing edge 28 is an extended position so as to engage with the manifold surface (not shown).
- FIG. 8 shows the open position of the valve 10 and armature 14 when voltage is applied to the coil 36 such that a force on the armature 14 overcomes the force of spring 44 . In this position, the sealing edge 28 is a retracted position so as to disengage with the manifold surface (not shown).
- a pressure balancing structure that includes a first, axially extending port 64 and a second port 66 extending transversely with respect to the first port 64 and in communication therewith.
- the first port 64 extends axially through the seal structure 22 , the gland member 18 and into the armature 14 and can be considered to be part of bore 41 in the armature 14 .
- the port 66 has a reduced diameter portion 65 in the armature 14 .
- the second port 66 extends transversely through the reduced diameter portion 65 to the outer periphery of the stem portion 55 of the armature 14 .
- the second port 66 allows pressure balance between the magnetic working gap area 62 and an area 68 adjacent to the diameter defining the sealing edge 28 .
- the first port 65 continues upward to the bore 41 that houses the spring 44 , balancing the pressure there.
- the bore 41 can be considered to be part of the first port 64 .
- the pressure balancing structure includes flats 70 in the periphery of the rod-shaped stem portion 55 of the armature 14 that create a passage communicating an area 72 adjacent to the distal end 74 of the armature 14 and proximal to the spring pin 40 , with the magnetic working gap area 62 .
- a pressure balance is permitted between the area 72 and the working gap area 62 .
- the ports 64 , 66 and flats 70 on the armature 14 are conveniently incorporated in a metal injection molded (MIM) part, as the flats are already added for knit line relief in the mold design. Passage sizes are roughly selected to provide pneumatic damping and smoothing of the opening and closing strokes.
- MIM metal injection molded
- the valve 10 is an electronically activated electromagnetic valve whose purpose is to bypass working air from the high pressure side to the low pressure side of a manifold pressure boost pump, turbocharger, supercharger, turbine air pump or similar.
- the air bypass valve 10 utilizes a novel passive internal pressure balancing method, reducing the noise of operation and reducing the force required to both open and close the valve.
- the air bypass valve provides the functionality for the success, long term operation and efficiency of air boost systems, which depend on responsiveness to dynamic changes and robustness of operation.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
- This application is based on U.S. Provisional Application No. 61/066,349 filed on Feb. 19, 2008, claims the benefit thereof for priority purposes, and is hereby incorporated by reference into this specification.
- The embodiment relates to a solenoid device for the bypass of intake air in an automotive application and, more particularly, to an air bypass valve that has passive internal pressure balancing.
- Automotive applications typically using an air pump, specifically a turbine, supercharger, or exhaust driven turbocharger, include gasoline, natural gas or diesel internal combustion engines. Other automotive applications also include fuel cells and fuel reformers, both requiring large volumes of air and often supplied by a turbine pump. While a bypass valve may be utilized for any pump configuration, the exhaust driven turbocharger is the typical application. The exhaust driven turbocharger is a free-spinning turbine with a shaft-separated split impeller, one end receiving force and a rotational moment from the exiting exhaust gases, the other end applying a pumping effect. As it is a free-spinning turbine, if the load on the air side suddenly increases due to a sudden decrease of demand by the engine, such as during deceleration, the pump will see a dramatic decrease in rotation and the corresponding sudden decrease in cooling effect, lubricating effect, as well as a high fatigue load on the impeller blades.
- For the purpose of reducing the load on the turbocharger during sudden decreases of downstream flow, a bypass valve is typically applied to allow the impeller to continue moving air from the low pressure side to the high pressure side at a rate now set by the impeller speed. It is desirable to have a valve which can respond quickly when deceleration, load change or load shift point occurs, and recover quickly as when acceleration or higher load is suddenly required. When not energized, it is desirable to minimize bypass leak and corresponding decrease in pump efficiency when full throughput is required from pump. This must be satisfied with robustness as well as cost efficiency, while at the same time not introducing undesirable noise, vibration and harshness, or noise, vibration, harshness (NVH). Historically, bypass valves are comparatively large, heavy electromagnets with machined parts and multiple elastomeric diaphragms, bumpers and seals.
- Thus, there is a need to provide an improved air bypass valve that reduces noise and reduces the force to open and close the valve.
- An object of the present invention is to fulfill the need referred to above. In accordance with the principles of an embodiment, this objective is obtained by providing a pressure-balanced solenoid device including a solenoid assembly having a stator and a coil constructed and arranged to be energized to generate a magnetic field. An armature and seal assembly includes an armature structure constructed and arranged to move with respect to the solenoid assembly from a closed position, defining a working gap area between the coil and a portion of the armature structure, to an open position in response to the magnetic field generated by the coil. The armature structure includes a proximal end and a distal end. The armature and seal structure also includes a seal structure coupled with proximal end of the armature structure. The seal structure has a sealing edge constructed and arranged to seal with a component when the armature structure is in the closed position thereof. A spring biases the armature structure to the closed position. The armature and seal assembly includes pressure balancing structure constructed and arranged to provide a pressure balance between the working gap area and an area defined adjacent to 1) the sealing edge, and 2) the distal end of the armature structure. The solenoid device may be an air bypass valve for an automobile.
- In accordance with another aspect of the embodiment, a method of balancing pressure in a solenoid device provides a solenoid assembly including a stator and a coil constructed and arranged to be energized to generate a magnetic field. An armature structure is provided and is constructed and arranged to move with respect to the solenoid assembly from a closed position, defining a working gap area between the coil and a portion of the armature structure, to an open position in response to the magnetic field generated by the coil. The armature structure includes a proximal end and a distal end. A seal structure is coupled with proximal end of the armature structure. The seal structure has a sealing edge constructed and arranged to seal with a component when the armature structure is in the closed position thereof. The armature structure is biased to the closed position. The method ensures that under certain operating conditions of the device, pressure is balanced between the working gap area and an area defined adjacent to 1) the sealing edge, and 2) the distal end of the armature structure.
- Other objects, features and characteristics of the present invention, as well as the methods of operation and the functions of the related elements of the structure, the combination of parts and economics of manufacture will become more apparent upon consideration of the following detailed description and appended claims with reference to the accompanying drawings, all of which form a part of this specification.
- The invention will be better understood from the following detailed description of the preferred embodiments thereof, taken in conjunction with the accompanying drawings, wherein like reference numerals refer to like parts, in which:
-
FIG. 1 is a view of a solenoid device in the form of an automotive air bypass valve in accordance with an embodiment of the present invention. -
FIG. 2 is an exploded view of an armature and seal assembly of the air bypass valve ofFIG. 1 . -
FIG. 3 is an assembled view of the armature and seal assembly ofFIG. 2 . -
FIG. 4 is an exploded view of a solenoid assembly of the air bypass valve ofFIG. 1 . -
FIG. 5 is an assembled view of the solenoid assembly ofFIG. 4 . -
FIG. 6 is an exploded view of the armature assembly being inserted into the overmolded solenoid assembly of the air bypass valve ofFIG. 1 . -
FIG. 7 is a sectional view of a solenoid device ofFIG. 1 shown with an armature in a closed position. -
FIG. 8 is a view of the solenoid device ofFIG. 7 , with the armature shown in an open position. - Referring to
FIG. 1 , a solenoid device in the form of an air bypass valve for a vehicle is shown, generally indicated at 10, in accordance with an embodiment of the invention. The air bypass valve detailed herein comprises about fourteen basic parts, potentially none of which are machined, but all of which are preferably injection molded, stamped, or drawn from sheet stock. Such a configuration provides a realized savings in used material volume and type, along with the corresponding environmental and economic benefits. - With reference to
FIGS. 2 , 3, and 7, an armature and seal assembly is shown, generally indicated at 12. The armature andseal assembly 12 is the moving component of thevalve 10 and includes an armature structure having anarmature 14 and a composite, resin or polymer moldedpivot gland structure 16 either molded onto aproximal end 15 of thearmature 14 or assembled thereto with a mechanical retainer (not shown). Thus, thegland structure 16 can be considered to be part of thearmature 14 and includes agland member 18, the function of which will be explained below. Adynamic seal 20 of an appropriate material is either incorporated as part of thegland structure 16, co-injection molded therewith, or coupled thereto as a separate component. Thedynamic seal 20 reduces air leakage past thearmature 14, reducing both air noise and bypass leakage. Finally, ahard seal structure 22, preferably made of similar materials as thegland structure 16, has apivot member 23 that is preferably snapped together with thegland member 18. As best shown inFIG. 7 , the mating co-centric spherical surfaces (external surface 24 ofgland member 18 andinternal surface 26 of the pivot member 23) form a pivot function such that theseal structure 22 can pivot with respect to thegland structure 16 and thus thearmature 14. The 360° pivot function is accommodates any dimensional variance from ideal between the axis of thesolenoid assembly 30, mounting face of the complete assembly and the sealing surface and mounting surfaces of the respective air manifold or component to which thevalve assembly 10 is attached. By accommodating these variances, bypass leak is minimized and durable function of the solenoid maximized in allowing the hard sealingedge 28 of thehard seal structure 22 to mate with the opposite mounting sealing surface as parallel as possible. It is noted that the inner spherical surface can be part of the gland member with the outer spherical surface being part of thepivot member 23. - With reference to
FIGS. 4 , 5, and 8, solenoid assembly, generally indicated at 30, is shown. Thesolenoid assembly 30 includes the stationary magnetic components of thevalve 10 and includes a magnetic (e.g., ferrous)housing 32 that provides a flux return path and a datum enclosure for other parts of thevalve 10. Acoil bobbin 34 is wound with anelectromagnet coil 36 of a suitable wire material of an appropriate number of turns to provide the resistance and ampere-turns necessary for proper function with the available control electronics. Thecoil 36 is not shown inFIG. 4 . Thecoil bobbin 34 withcoil 36 is inserted into thehousing 32, and a magnetic (e.g., ferrous)flux ring 38 is pressed into thehousing 32, retaining thecoil bobbin 34 and providing a specific working magnetic pole-type to thearmature 14. Aspring pin 40 is provided in thehousing 32 and a magnetic (e.g., ferrous)end cap 42 is pressed onto thehousing 32, thereby retaining thespring pin 40. As shown inFIG. 7 , upon assembly, thespring pin 40 is received in abore 41 in astem portion 55 of thearmature 14 so that afirst end 43 of thespring pin 40 engages thespring 44 and asecond end 45 of thespring pin 40 is adjacent to theend cap 42. Thespring pin 40 provides an axial flux path into thearmature 14 as well as guides aclosing return spring 44, also inbore 41, in the final assembly. The stator of thesolenoid assembly 30 comprises the lump magnetic circuit formed by themagnetic flux ring 38, themagnetic housing 32, themagnetic end cap 42 and, if desired, thespring pin 40. - With reference to
FIG. 6 , thesolenoid assembly 30 is over-molded with an appropriate polymer or resin to provide the final encapsulation and retentionmain housing 46 of all stationary parts for theair bypass valve 10.FIG. 6 shows the final assembly of thevalve 10 and also shows how the encapsulation provides a customer specifiedflange 48 for mounting by the end user. Preferably theflange 48 includes mountingholes 50 that receive, preferably in an encapsulated manner, asupport boss 52 therein. In addition, themain housing 46 includes impact protection structure that protect the armature and sealassembly 12 from drops and handling, as well as any manifold sealing O-rings. In the embodiment, the impact protection structure includes a plurality oftabs 54 extending in an annular manner from abottom surface 56 of thehousing 46 so as to generally surround theseal structure 22 of the armature and sealassembly 12. - In the final assembly steps, the
closing return spring 44 is inserted into thearmature 14, and the armature and sealassembly 12 is the inserted into thesolenoid assembly 30. More particularly, astem portion 55 of thearmature 14 is received in abore 57 in thecoil bobbin 34. An O-ring 58 provides a seal with respect to an air manifold (not shown) to which thevalve 10 is attached. - Basic operation of the
valve 10 will be appreciated with reference toFIGS. 7 and 8 .FIG. 7 shows the closed position thevalve 10 and armature 14 (biased by spring 44) when theelectromagnetic coil 36 is not energized via leads 60. In this position, the magnetic gap workingvolume area 62 is clearly shown between thecoil 36 and a generallycylindrical base 63 of thearmature 14. The sealingedge 28 is an extended position so as to engage with the manifold surface (not shown).FIG. 8 shows the open position of thevalve 10 andarmature 14 when voltage is applied to thecoil 36 such that a force on thearmature 14 overcomes the force ofspring 44. In this position, the sealingedge 28 is a retracted position so as to disengage with the manifold surface (not shown). - As best shown in
FIG. 7 , advantageous passive internal pressure balance is realized through air passing into a pressure balancing structure that includes a first, axially extendingport 64 and asecond port 66 extending transversely with respect to thefirst port 64 and in communication therewith. Thefirst port 64 extends axially through theseal structure 22, thegland member 18 and into thearmature 14 and can be considered to be part ofbore 41 in thearmature 14. Theport 66 has a reduceddiameter portion 65 in thearmature 14. Thesecond port 66 extends transversely through the reduceddiameter portion 65 to the outer periphery of thestem portion 55 of thearmature 14. Thesecond port 66 allows pressure balance between the magnetic workinggap area 62 and anarea 68 adjacent to the diameter defining the sealingedge 28. Thefirst port 65 continues upward to thebore 41 that houses thespring 44, balancing the pressure there. Thebore 41 can be considered to be part of thefirst port 64. - Finally, the pressure balancing structure includes
flats 70 in the periphery of the rod-shapedstem portion 55 of thearmature 14 that create a passage communicating anarea 72 adjacent to thedistal end 74 of thearmature 14 and proximal to thespring pin 40, with the magnetic workinggap area 62. Thus, a pressure balance is permitted between thearea 72 and the workinggap area 62. Theports flats 70 on thearmature 14 are conveniently incorporated in a metal injection molded (MIM) part, as the flats are already added for knit line relief in the mold design. Passage sizes are roughly selected to provide pneumatic damping and smoothing of the opening and closing strokes. - Thus, the
valve 10 is an electronically activated electromagnetic valve whose purpose is to bypass working air from the high pressure side to the low pressure side of a manifold pressure boost pump, turbocharger, supercharger, turbine air pump or similar. Theair bypass valve 10 utilizes a novel passive internal pressure balancing method, reducing the noise of operation and reducing the force required to both open and close the valve. The air bypass valve provides the functionality for the success, long term operation and efficiency of air boost systems, which depend on responsiveness to dynamic changes and robustness of operation. - The foregoing preferred embodiments have been shown and described for the purposes of illustrating the structural and functional principles of the present invention, as well as illustrating the methods of employing the preferred embodiments and are subject to change without departing from such principles. Therefore, this invention includes all modifications encompassed within the spirit of the following claims.
Claims (16)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/812,603 US8348231B2 (en) | 2008-02-19 | 2009-02-17 | Pressure balance of automotive air bypass valve |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US6634908P | 2008-02-19 | 2008-02-19 | |
PCT/US2009/034227 WO2009108531A1 (en) | 2008-02-19 | 2009-02-17 | Pressure balance of automotive air bypass valve |
US12/812,603 US8348231B2 (en) | 2008-02-19 | 2009-02-17 | Pressure balance of automotive air bypass valve |
Publications (2)
Publication Number | Publication Date |
---|---|
US20100288953A1 true US20100288953A1 (en) | 2010-11-18 |
US8348231B2 US8348231B2 (en) | 2013-01-08 |
Family
ID=40834316
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/812,603 Expired - Fee Related US8348231B2 (en) | 2008-02-19 | 2009-02-17 | Pressure balance of automotive air bypass valve |
Country Status (2)
Country | Link |
---|---|
US (1) | US8348231B2 (en) |
WO (1) | WO2009108531A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100148103A1 (en) * | 2008-12-15 | 2010-06-17 | Continental Automotive Systems Us, Inc. | Automobile high pressure pump solenoid valve |
US20100147266A1 (en) * | 2008-12-15 | 2010-06-17 | Continental Automotive Systems Us, Inc. | Automotive high pressure pump solenoid valve with limp home calibration |
CN107076013A (en) * | 2014-09-19 | 2017-08-18 | 皮尔伯格有限责任公司 | Inertia circulating air valve for the compressor of internal combustion engine |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009108533A2 (en) | 2008-02-19 | 2009-09-03 | Continental Automotive Systems Us, Inc. | Tau-omega armature-stator configuration of long stroke solenoid |
WO2009105405A1 (en) | 2008-02-19 | 2009-08-27 | Continental Automotive Systems Us, Inc. | Lift lock assembly feature for air bypass valve |
US9157545B2 (en) | 2008-02-19 | 2015-10-13 | Continental Automotive Systems, Inc. | Automotive air bypass valve |
DE102010063727B4 (en) * | 2010-12-21 | 2019-05-23 | Robert Bosch Gmbh | magnetic valve |
DE102011016276A1 (en) * | 2011-04-06 | 2012-10-11 | Eagle Actuator Components Gmbh & Co. Kg | Valve for use in turbo supercharger of motor car, has sealing ring arranged between peripheral surface of sealing device and inner wall of housing, and actuator device that moves valve body, where ring is movably secured at sealing device |
DE102011116393B3 (en) * | 2011-10-20 | 2013-01-03 | Dynamic Systems S.A. | Pilot stage of a proportionally controlled hydraulic valve |
NL2009504C2 (en) * | 2012-09-24 | 2014-03-25 | Daf Trucks Nv | Suspension system for a driver's compartment of a vehicle. |
US10871242B2 (en) | 2016-06-23 | 2020-12-22 | Rain Bird Corporation | Solenoid and method of manufacture |
US10119628B1 (en) * | 2017-04-19 | 2018-11-06 | Schaeffler Technologies AG & Co. KG | Pressure compensated switching solenoid valve |
US10980120B2 (en) | 2017-06-15 | 2021-04-13 | Rain Bird Corporation | Compact printed circuit board |
US10662904B2 (en) | 2018-03-30 | 2020-05-26 | Deere & Company | Exhaust manifold |
US11073076B2 (en) | 2018-03-30 | 2021-07-27 | Deere & Company | Exhaust manifold |
US11503782B2 (en) | 2018-04-11 | 2022-11-22 | Rain Bird Corporation | Smart drip irrigation emitter |
JP7115328B2 (en) * | 2019-01-15 | 2022-08-09 | 株式会社デンソー | solenoid valve |
KR20210000476A (en) * | 2019-06-25 | 2021-01-05 | 현대자동차주식회사 | Fuel supply valve |
US11721465B2 (en) | 2020-04-24 | 2023-08-08 | Rain Bird Corporation | Solenoid apparatus and methods of assembly |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2596409A (en) * | 1947-03-14 | 1952-05-13 | A P Controls Corp | Solenoid gas valve |
US4610428A (en) * | 1985-03-11 | 1986-09-09 | Borg-Warner Automotive, Inc. | Hermetically sealed electromagnetic solenoid valve |
US5875922A (en) * | 1997-10-10 | 1999-03-02 | Nordson Corporation | Apparatus for dispensing an adhesive |
DE10020041A1 (en) * | 2000-04-22 | 2001-10-25 | Pierburg Ag | Bypass valve body for turbo internal combustion engine has valve head and valve rod both with at least one pressure equalization bore, electrically actuated drive system for valve rod |
US20070228311A1 (en) * | 2006-03-28 | 2007-10-04 | Beneker Gerrit V | Pressure balanced valve |
US20090045364A1 (en) * | 2005-12-01 | 2009-02-19 | Borgwarner Inc. | Pressure Compensating Method |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004044439B4 (en) * | 2004-09-14 | 2006-09-21 | A. Kayser Automotive Systems Gmbh | Blow-off valve for a turbocharger |
DE102004053849A1 (en) * | 2004-11-04 | 2006-05-11 | Robert Bosch Gmbh | Recirculation valve for turbocharger internal combustion engines |
DE102005028141A1 (en) * | 2005-06-17 | 2006-12-28 | Robert Bosch Gmbh | Bypass valve for internal combustion engines |
PL1941138T3 (en) | 2005-10-29 | 2010-06-30 | Pierburg Gmbh | Ambient-air pulsed valve for internal combustion engines equipped with a turbocharger |
US9157545B2 (en) | 2008-02-19 | 2015-10-13 | Continental Automotive Systems, Inc. | Automotive air bypass valve |
WO2009108533A2 (en) | 2008-02-19 | 2009-09-03 | Continental Automotive Systems Us, Inc. | Tau-omega armature-stator configuration of long stroke solenoid |
WO2009105405A1 (en) | 2008-02-19 | 2009-08-27 | Continental Automotive Systems Us, Inc. | Lift lock assembly feature for air bypass valve |
-
2009
- 2009-02-17 US US12/812,603 patent/US8348231B2/en not_active Expired - Fee Related
- 2009-02-17 WO PCT/US2009/034227 patent/WO2009108531A1/en active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2596409A (en) * | 1947-03-14 | 1952-05-13 | A P Controls Corp | Solenoid gas valve |
US4610428A (en) * | 1985-03-11 | 1986-09-09 | Borg-Warner Automotive, Inc. | Hermetically sealed electromagnetic solenoid valve |
US5875922A (en) * | 1997-10-10 | 1999-03-02 | Nordson Corporation | Apparatus for dispensing an adhesive |
DE10020041A1 (en) * | 2000-04-22 | 2001-10-25 | Pierburg Ag | Bypass valve body for turbo internal combustion engine has valve head and valve rod both with at least one pressure equalization bore, electrically actuated drive system for valve rod |
US20090045364A1 (en) * | 2005-12-01 | 2009-02-19 | Borgwarner Inc. | Pressure Compensating Method |
US20070228311A1 (en) * | 2006-03-28 | 2007-10-04 | Beneker Gerrit V | Pressure balanced valve |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100148103A1 (en) * | 2008-12-15 | 2010-06-17 | Continental Automotive Systems Us, Inc. | Automobile high pressure pump solenoid valve |
US20100147266A1 (en) * | 2008-12-15 | 2010-06-17 | Continental Automotive Systems Us, Inc. | Automotive high pressure pump solenoid valve with limp home calibration |
US8317157B2 (en) * | 2008-12-15 | 2012-11-27 | Continental Automotive Systems Us, Inc. | Automobile high pressure pump solenoid valve |
US8328158B2 (en) * | 2008-12-15 | 2012-12-11 | Continental Automotive Systems Us, Inc. | Automotive high pressure pump solenoid valve with limp home calibration |
CN107076013A (en) * | 2014-09-19 | 2017-08-18 | 皮尔伯格有限责任公司 | Inertia circulating air valve for the compressor of internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
US8348231B2 (en) | 2013-01-08 |
WO2009108531A1 (en) | 2009-09-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8348231B2 (en) | Pressure balance of automotive air bypass valve | |
US9157545B2 (en) | Automotive air bypass valve | |
US8443829B2 (en) | Lift lock assembly feature for air bypass valve | |
US8678343B2 (en) | Tau-omega armature-stator configuration of long stroke solenoid | |
KR101570141B1 (en) | Bearing housing body group of an exhaust-gas turbocharger | |
US9353706B2 (en) | Actuator and valve arrangement | |
US20090087302A1 (en) | Turbocharger | |
CN106605051B (en) | Solenoid valve for an internal combustion engine | |
WO2014068765A1 (en) | Valve | |
US10495232B2 (en) | Dual path dual purge valve system and valve assembly for turbo boosted engine | |
WO2014102133A1 (en) | Compressed-gas bypass valven | |
WO2013036572A1 (en) | High flow outward opening gaseous injector for automotive applications | |
EP3663571B1 (en) | Fuel pump and inlet valve assembly thereof | |
US10087827B2 (en) | Valve device for vehicle | |
US6651951B2 (en) | Magnetic valve | |
US8616473B2 (en) | High flow compressed natural gas injector for automotive applications | |
WO2017216957A1 (en) | Air bypass valve | |
WO2014179316A2 (en) | Blow off valve and related system and method | |
JP2024518130A (en) | FUEL PUMP HAVING INLET VALVE ASSEMBLY - Patent application | |
JP2006526118A (en) | A control device for an electropneumatic pressure transducer. | |
US11885430B2 (en) | Electromechanical valve and method of assembly | |
WO2021191842A1 (en) | Ultra-low leak electrical compressor bypass valve with soft seal and non-detachable poppet |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: CONTINENTAL AUTOMOTIVE SYSTEMS US, INC., MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CZIMMEK, PERRY ROBERT;HORNBY, MICHAEL J.;REEL/FRAME:024669/0582 Effective date: 20090216 |
|
FEPP | Fee payment procedure |
Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
AS | Assignment |
Owner name: CONTINENTAL AUTOMOTIVE SYSTEMS, INC., MICHIGAN Free format text: MERGER;ASSIGNOR:CONTINENTAL AUTOMOTIVE SYSTEMS US, INC.;REEL/FRAME:033034/0225 Effective date: 20121212 |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
FEPP | Fee payment procedure |
Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
LAPS | Lapse for failure to pay maintenance fees |
Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20210108 |